CN115853978A - Gear box - Google Patents
Gear box Download PDFInfo
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- CN115853978A CN115853978A CN202310067446.5A CN202310067446A CN115853978A CN 115853978 A CN115853978 A CN 115853978A CN 202310067446 A CN202310067446 A CN 202310067446A CN 115853978 A CN115853978 A CN 115853978A
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- clutch
- gear
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- planetary row
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Abstract
The present disclosure relates to vehicle technology, and more particularly to a transmission. This gearbox includes: the input shaft is connected with the sun gear of the first planet row and the sun gear of the second planet row respectively, the input shaft is connected with the sun gear of the third planet row and the sun gear of the fourth planet row respectively through the first clutch, and the input shaft is connected with the planet carrier of the third planet row through the second clutch. This gearbox, the third clutch keeps off with the second keeps off all in the bonding state advancing at first, therefore the third clutch need bear great moment of torsion, and with the planet carrier and the gearbox casing fixed connection of first planet row, on the ring gear output moment of torsion through first planet row reaches the third clutch, can reduce the moment of torsion that the third clutch will bear when combining effectively, guarantee whole gearbox most stable and reliability then, prevent the condition such as the low gear clutch slides and rubs, influence driving safety.
Description
Technical Field
The present disclosure relates to vehicle technology, and more particularly to a transmission.
Background
The automobile gearbox is a set of speed changing devices used for coordinating the rotating speed of an engine and the actual running speed of wheels, and is used for exerting the optimal performance of the engine. The gearbox can generate different gear ratios between an engine and wheels in the running process of the automobile, so that the transmission of different gear rotating speeds is realized.
The manual gearbox mainly comprises gears and a rotating shaft, and the speed change and torque change are generated by different gear combinations; the automatic gearbox AT consists of a hydraulic torque converter, a planetary gear and a hydraulic control system, and achieves the purposes of speed and torque changing through a hydraulic transmission and gear combination mode.
Among them, the automatic transmission has advantages of comfortable driving, reducing fatigue of driver, etc., and has become a development direction of modern vehicle configuration. The automatic gearbox utilizes a planetary gear mechanism to change speed, can automatically change speed according to the degree of an accelerator pedal and the change of vehicle speed, and a driver only needs to operate the accelerator pedal to control the vehicle speed, so that the driver can watch road traffic with full attention without being confused by gear shifting.
However, the existing transmission applied to a truck, a truck and other vehicles with large torque often causes the condition that a clutch and a brake are out of work due to large torque and overlarge load of an engine of the vehicle in a low gear, and the reliability and the stability of the whole transmission are affected.
Disclosure of Invention
In order to solve the technical problem, the present disclosure provides a transmission.
In a first aspect, the present disclosure provides a gearbox comprising: the planetary transmission mechanism comprises a first planetary row, a second planetary row, a third planetary row, a fourth planetary row, a first clutch, a second clutch, a third clutch, a first brake, a second brake, a third brake, an input shaft and an output shaft;
the input shaft is connected with the sun gear of the first planet row and the sun gear of the second planet row respectively, the input shaft is connected with the sun gear of the third planet row and the sun gear of the fourth planet row respectively through the first clutch, the input shaft is connected with the planet carrier of the third planet row through the second clutch, and the output shaft is connected with the planet carrier of the fourth planet row;
the planet carrier of the first planet row is connected with a gearbox shell, and the gear ring of the first planet row is connected with the planet carrier of the second planet row through the third clutch;
the gear ring of the second planet row is connected with the gearbox shell through the first brake, and the planet carrier of the second planet row is connected with the gear ring of the third planet row;
the gear ring of the third planetary row is connected with the gearbox shell through the second brake, and the planet carrier of the third planetary row is connected with the gear ring of the fourth planetary row;
and the gear ring of the fourth planetary row is connected with the gearbox shell through the third brake.
Optionally, the sun gear of the first planet row and the sun gear of the second planet row are connected through a first transmission member, and the first transmission member is connected with the input shaft.
Optionally, the sun gear of the third planetary row and the sun gear of the fourth planetary row are connected through a second transmission, and the input shaft is connected with the second transmission through the first clutch.
Optionally, the first planet row, the second planet row, the third planet row and the fourth planet row are sequentially arranged.
Optionally, the first planet row, the second planet row, the third planet row, and the fourth planet row are coaxially arranged.
Optionally, closing the third clutch and the third brake to form a first forward gear;
closing the first clutch and the third brake to form a second forward gear;
closing the first clutch and the third clutch to form a third forward gear;
closing the first clutch and the second brake to form a fourth forward gear;
closing the first clutch and the first brake to form a fifth forward gear;
closing the first clutch and the second clutch to form a sixth forward gear;
closing the second clutch and the first brake to form a seventh forward gear;
closing the second clutch and the second brake to form an eighth forward gear;
closing the second clutch and the third clutch to form a ninth forward gear;
closing the first brake and the third brake to form a reverse gear.
Compared with the prior art, the technical scheme provided by the embodiment of the disclosure has the following advantages:
the gearbox provided by the disclosure forms a gearbox with nine forward gears and one reverse gear through the combination of four planet rows, three clutches and three brakes, and it needs to be explained that the third clutch is in a combined state at the first forward gear and the second forward gear, so the third clutch needs to bear larger torque, and the planet carrier of the first planet row is fixedly connected with the gearbox shell, and the torque is output to the third clutch through the gear ring of the first planet row, so that the torque to be borne when the third clutch is combined can be effectively reduced, and then the most stability and reliability of the whole gearbox are ensured, thereby preventing the conditions of low-gear clutch sliding friction and the like, and affecting the driving safety.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present disclosure and, together with the description, serve to explain the principles of the disclosure.
In order to more clearly illustrate the embodiments or technical solutions in the prior art of the present disclosure, the drawings used in the description of the embodiments or prior art will be briefly described below, and it is obvious for those skilled in the art that other drawings can be obtained according to the drawings without inventive exercise.
FIG. 1 is a schematic structural diagram of a transmission according to an embodiment of the present disclosure;
fig. 2 is a shift logic diagram of a transmission according to an embodiment of the present disclosure.
11, a first planet row; 12. a second planet row; 13. a third planet row; 14. a fourth planet row; 21. a first clutch; 22. a second clutch; 23. a third clutch; 31. a first brake; 32. a second brake; 33. a third brake; 4. a gearbox housing.
Detailed Description
In order that the above objects, features and advantages of the present disclosure may be more clearly understood, aspects of the present disclosure will be further described below. It should be noted that the embodiments and features of the embodiments of the present disclosure may be combined with each other without conflict.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present disclosure, but the present disclosure may be practiced otherwise than as described herein; it is to be understood that the embodiments disclosed in the specification are only a few embodiments of the present disclosure, and not all embodiments.
The automobile gearbox is a set of speed changing devices used for coordinating the rotating speed of an engine and the actual running speed of wheels, and is used for exerting the optimal performance of the engine. The gearbox can generate different gear ratios between an engine and wheels in the running process of the automobile, so that the transmission of different gear rotating speeds is realized.
The manual gearbox mainly comprises gears and a rotating shaft, and the speed change and torque change are generated by different gear combinations; the automatic gearbox AT consists of a hydraulic torque converter, a planetary gear and a hydraulic control system, and achieves the purposes of speed and torque changing through a hydraulic transmission and gear combination mode.
Among them, the automatic transmission has advantages of comfortable driving, reducing fatigue of driver, etc., and has become a development direction of modern vehicle configuration. The automatic gearbox utilizes a planetary gear mechanism to change speed, can automatically change speed according to the degree of an accelerator pedal and the change of vehicle speed, and a driver only needs to operate the accelerator pedal to control the vehicle speed, so that the driver can watch road traffic with full attention without being confused by gear shifting.
However, the existing transmission applied to a truck, a truck and other vehicles with large torque often causes the condition that a clutch and a brake are out of work due to large torque and overlarge load of an engine of the vehicle in a low gear, and the reliability and the stability of the whole transmission are affected.
Based on this, the embodiment provides a gearbox, a gearbox with nine forward gears and one reverse gear is formed by combining four planet rows, three clutches and three brakes, it should be noted that the third clutch is in a combined state at both the first forward gear and the second forward gear, so the third clutch needs to bear a large torque, the planet carrier of the first planet row is fixedly connected with the gearbox shell, and the torque to be borne when the third clutch is combined can be effectively reduced by outputting the torque to the third clutch through the gear ring of the first planet row, so that the most stability and reliability of the whole gearbox are ensured, the conditions of slipping and friction of the low-gear clutch and the like are prevented, and the driving safety is affected. This is illustrated in detail by the following specific examples:
referring to fig. 1 and 2, the present embodiment provides a transmission including: a first planetary row 11, a second planetary row 12, a third planetary row 13, a fourth planetary row 14, a first clutch 21, a second clutch 22, a third clutch 23, a first brake 31, a second brake 32, a third brake 33, an input shaft and an output shaft; the input shaft is respectively connected with the sun gear of the first planet row 11 and the sun gear of the second planet row 12, the input shaft is respectively connected with the sun gear of the third planet row 13 and the sun gear of the fourth planet row 14 through a first clutch 21, the input shaft is connected with the planet carrier of the third planet row 13 through a second clutch 22, and the output shaft is connected with the planet carrier of the fourth planet row 14; the planet carrier of the first planet row 11 is connected with the gearbox shell 4, and the gear ring of the first planet row 11 is connected with the planet carrier of the second planet row 12 through a third clutch 23; the ring gear of the second planetary gear set 12 is connected with the gearbox housing 4 through a first brake 31, and the planet carrier of the second planetary gear set 12 is connected with the ring gear of the third planetary gear set 13; the ring gear of the third planetary row 13 is connected with the gearbox housing 4 through a second brake 32, and the planet carrier of the third planetary row 13 is connected with the ring gear of the fourth planetary row 14; the ring gear of the fourth planetary gear set 14 is connected to the transmission housing 4 via a third brake 33.
The gearbox with nine forward gears and one reverse gear is formed by combining four planetary rows, three clutches and three brakes, and it should be noted that the third clutch 23 is in a combined state at both the first forward gear and the second forward gear, so that the third clutch 23 needs to bear a large torque, the planet carrier of the first planetary row 11 is fixedly connected with the gearbox shell 4, and the torque to be borne when the third clutch 23 is combined can be effectively reduced by outputting the torque to the third clutch 23 through the gear ring of the first planetary row 11, so that the maximum stability and reliability of the whole gearbox are ensured, the situations of low-gear clutch sliding friction and the like are prevented, and the driving safety is influenced.
In some embodiments, the sun gear of the first planetary row 11 and the sun gear of the second planetary row 12 are connected by a first transmission member, which is connected to the input shaft; in a further embodiment, the sun gear of the third planetary row 13 and the sun gear of the fourth planetary row 14 are connected by a second transmission, to which the input shaft is connected by a first clutch 21; it should be understood that the first transmission element and the second transmission element are specifically a structure capable of simultaneously connecting the sun gears of the two planet rows in a transmission manner, that is, when the input shaft transmits a torque to the first transmission element or the second transmission element, the first transmission element or the second transmission element can simultaneously drive the sun gears of the two planet rows connected with the first transmission element or the second transmission element to synchronously rotate, and the first transmission element and the second transmission element can be fixedly connected with the sun gears in a welding manner, a bolt connection manner, or the like; through the setting of first driving medium and second driving medium, can show and simplify whole transmission structure, guarantee the reliability of gearbox, simultaneously, when the input shaft transmits the moment of torsion for the sun gear of two planet rows simultaneously, can not lose partial moment of torsion by first driving medium or second driving medium to guarantee the transmission efficiency of gearbox.
In some embodiments, the first planet row 11, the second planet row 12, the third planet row 13, and the fourth planet row 14 are arranged in sequence; in a further embodiment, the first, second, third and fourth planetary rows 11, 12, 13, 14 are arranged coaxially; it should be noted that, the first planet row 11, the second planet row 12, the third planet row 13 and the fourth planet row 14 are arranged inside the gearbox in this way, so that the play between the four planet rows in the radial direction can be reduced when torque is transmitted, the four planet rows are connected in sequence, and the two connected planet rows can be in a radial limit structure, that is, the gear ring of the first planet row 11 and the planet carrier of the second planet row 12 can be in a radial limit structure, so as to form a reliable and stable planet row system.
As shown in fig. 1 and 2, in fig. 2, C1 is a first clutch 21, C2 is a second clutch 22, C3 is a third clutch 23, B1 is a first brake 31, B2 is a second brake 32, B3 is a third brake 33, D1 is a first forward gear, D2 is a second forward gear, D3 is a third forward gear, D4 is a fourth forward gear, D5 is a fifth forward gear, D6 is a sixth forward gear, D7 is a seventh forward gear, D8 is an eighth forward gear, D9 is a ninth forward gear, and R is a reverse gear;
closing the third clutch 23 and the third brake 33 to form a first forward gear; closing the first clutch 21 and the third brake 33 to form a second forward gear; closing the first clutch 21 and the third clutch 23 to form a third forward gear; closing the first clutch 21 and the second brake 32 to form a fourth forward gear; closing the first clutch 21 and the first brake 31 to form a fifth forward gear; closing the first clutch 21 and the second clutch 22 to form a sixth forward gear; closing the second clutch 22 and the first brake 31 to form a seventh forward gear; closing the second clutch 22 and the second brake 32 to form an eighth forward gear; closing the second clutch 22 and the third clutch 23 to form a ninth forward gear; closing the first brake 31 and the third brake 33 to form a reverse gear; the gear shifting logic can ensure the reasonability of the gear ratio of the gearbox, simultaneously can only switch one of the two gear shifting structures at each time of gear shifting, and the other gear shifting structure continuously keeps a combination state, namely, only one of two clutches, two brakes or one clutch of one brake needs to be cut off at each time of gear shifting, then the clutch is replaced by a new brake or the new clutch is combined, and the other clutch always keeps the combination state.
The specific implementation manner and implementation principle are the same as those of the above embodiments, and the same or similar technical effects can be brought, which are not described herein any more, and reference may be made to the description of the above transmission embodiment.
It is noted that, in this document, relational terms such as "first" and "second," and the like, are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrases "comprising a," "8230," "8230," or "comprising" does not exclude the presence of additional like elements in a process, method, article, or apparatus that comprises the element.
The foregoing are merely exemplary embodiments of the present disclosure, which enable those skilled in the art to understand or practice the present disclosure. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the disclosure. Thus, the present disclosure is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (6)
1. A transmission, comprising: the planetary transmission mechanism comprises a first planetary row (11), a second planetary row (12), a third planetary row (13), a fourth planetary row (14), a first clutch (21), a second clutch (22), a third clutch (23), a first brake (31), a second brake (32), a third brake (33), an input shaft and an output shaft;
the input shafts are respectively connected with the sun gear of the first planetary row (11) and the sun gear of the second planetary row (12), the input shafts are respectively connected with the sun gear of the third planetary row (13) and the sun gear of the fourth planetary row (14) through the first clutch (21), the input shafts are connected with the planet carrier of the third planetary row (13) through the second clutch (22), and the output shafts are connected with the planet carrier of the fourth planetary row (14);
the planet carrier of the first planet row (11) is connected with a transmission shell (4), and the gear ring of the first planet row (11) is connected with the planet carrier of the second planet row (12) through the third clutch (23);
the ring gear of the second planetary row (12) is connected with a gearbox shell (4) through the first brake (31), and the planet carrier of the second planetary row (12) is connected with the ring gear of the third planetary row (13);
the gear ring of the third planetary row (13) is connected with a gearbox shell (4) through the second brake (32), and the planet carrier of the third planetary row (13) is connected with the gear ring of the fourth planetary row (14);
the ring gear of the fourth planetary row (14) is connected with the gearbox housing (4) through the third brake (33).
2. The gearbox according to claim 1, characterised in that the sun wheel of the first planetary row (11) and the sun wheel of the second planetary row (12) are connected by a first transmission member, which is connected to the input shaft.
3. Gearbox according to claim 1, characterised in that the sun wheel of the third planetary row (13) and the sun wheel of the fourth planetary row (14) are connected by a second transmission, the input shaft being connected with the second transmission by the first clutch (21).
4. Gearbox according to claim 1, characterised in that said first planetary row (11), said second planetary row (12), said third planetary row (13) and said fourth planetary row (14) are arranged in sequence.
5. Gearbox according to claim 4, characterised in that said first planetary row (11), said second planetary row (12), said third planetary row (13) and said fourth planetary row (14) are coaxially arranged.
6. The gearbox of claim 1,
-closing the third clutch (23) and the third brake (33) to form a first forward gear;
-closing the first clutch (21) and the third brake (33) to form a second forward gear;
-closing the first clutch (21) and the third clutch (23) to form a third forward gear;
-closing the first clutch (21) and the second brake (32) to form a fourth forward gear;
-closing the first clutch (21) and the first brake (31) to form a fifth forward gear;
closing the first clutch (21) and the second clutch (22) to form a sixth forward gear;
closing the second clutch (22) and the first brake (31) to form a seventh forward gear;
closing the second clutch (22) and the second brake (32) to form an eighth forward gear;
-closing the second clutch (22) and the third clutch (23) to form a ninth forward gear;
closing the first brake (31) and the third brake (33) to form a reverse gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310067446.5A CN115853978B (en) | 2023-02-06 | 2023-02-06 | Gear box |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310067446.5A CN115853978B (en) | 2023-02-06 | 2023-02-06 | Gear box |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN115853978A true CN115853978A (en) | 2023-03-28 |
| CN115853978B CN115853978B (en) | 2023-05-16 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202310067446.5A Active CN115853978B (en) | 2023-02-06 | 2023-02-06 | Gear box |
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| Country | Link |
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| CN (1) | CN115853978B (en) |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009020442A1 (en) * | 2009-05-08 | 2010-11-11 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Transmission for internal combustion engine, has four planetary gears sets with sun wheels, planet wheel carriers, hollow wheels and six switching elements, where hollow wheel of third set is constantly connected to carrier of fourth set |
| DE102009028670A1 (en) * | 2009-08-20 | 2011-02-24 | Zf Friedrichshafen Ag | Planetary type multi-ratio transmission i.e. automatic transmission for passenger car, has shaft connected with sun wheels of two planetary sets and coupled to housing by brake, and driven shaft connected with bar of one of planetary sets |
| DE102009047273A1 (en) * | 2009-11-30 | 2011-06-01 | Zf Friedrichshafen Ag | Multistage planetary transmission i.e. automatic transmission, for e.g. passenger car, has planetary gear set with bar connected with output shaft, which is connected with another planetary gear set |
| WO2014000940A1 (en) * | 2012-06-26 | 2014-01-03 | Zf Friedrichshafen Ag | Multi-speed gearbox |
| DE102013205382A1 (en) * | 2013-03-27 | 2014-10-02 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
| CN104595436A (en) * | 2015-02-13 | 2015-05-06 | 中国北方车辆研究所 | Seven-gear planetary transmission for automatic transmission case |
| CN112324876A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission with large speed ratio range |
| CN112324877A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission |
-
2023
- 2023-02-06 CN CN202310067446.5A patent/CN115853978B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009020442A1 (en) * | 2009-05-08 | 2010-11-11 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Transmission for internal combustion engine, has four planetary gears sets with sun wheels, planet wheel carriers, hollow wheels and six switching elements, where hollow wheel of third set is constantly connected to carrier of fourth set |
| DE102009028670A1 (en) * | 2009-08-20 | 2011-02-24 | Zf Friedrichshafen Ag | Planetary type multi-ratio transmission i.e. automatic transmission for passenger car, has shaft connected with sun wheels of two planetary sets and coupled to housing by brake, and driven shaft connected with bar of one of planetary sets |
| DE102009047273A1 (en) * | 2009-11-30 | 2011-06-01 | Zf Friedrichshafen Ag | Multistage planetary transmission i.e. automatic transmission, for e.g. passenger car, has planetary gear set with bar connected with output shaft, which is connected with another planetary gear set |
| WO2014000940A1 (en) * | 2012-06-26 | 2014-01-03 | Zf Friedrichshafen Ag | Multi-speed gearbox |
| DE102013205382A1 (en) * | 2013-03-27 | 2014-10-02 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
| CN104595436A (en) * | 2015-02-13 | 2015-05-06 | 中国北方车辆研究所 | Seven-gear planetary transmission for automatic transmission case |
| CN112324876A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission with large speed ratio range |
| CN112324877A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission |
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| CN115853978B (en) | 2023-05-16 |
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